DE3819812A1 - ANTI-BLOCKING CONTROL SYSTEM - Google Patents

Description

State of the art

The invention relates to an anti-lock control system according to Genus of the main claim. Such an anti-lock control system is known (DE-PS 17 55 965). With this known anti-lock protection control system is controlled by a hydraulically controlled Switching valve actuated return device from a pressure medium one between the valve arrangement of at least one wheel brake cylinder ders and the conveyor arranged relief line in promoted a brake line. It can be assumed that, that the switching controlled by a certain relief pressure valve with the associated conveyor at an occurring Anti-lock control case, which has a large proportion of pressure medium quickly into the discharge line, reacting too slowly and does not make the necessary rapid pressure reduction possible.

Advantages of the invention

Label the anti-lock control system according to the invention with the features of the main claim has the advantage that the conveyor required during the pressure reduction by the valve-controlled piston pump is formed and thus from the wheel  brake fluid to be removed immediately in and Feeds back the direction of the brake line.

The measures listed in the subclaims provide for partial training and improvements in the main claim specified anti-lock control system possible.

A mounted in the conveyor is particularly advantageous Pump piston which, in the event of traction control, takes up a minimum of pressure medium least can promote a wheel brake cylinder.

Another advantage is the additional connection of the pressure with tel pump on a hydraulic brake booster.

drawing

Embodiments of the invention are shown in the drawing and explained in more detail in the following description. In the drawings Fig. 1 shows a first embodiment of an inventively stalteten anti-lock control, Fig. 2 shows a second exporting approximately example an inventively designed anti-lock control, Fig. 3 shows a third embodiment of an OF INVENTION dung configured according to the anti-lock control system, and Fig. 4 shows a fourth embodiment of the invention designed according to the anti-lock control system.

Description of the embodiments

An anti-lock control system 100 for vehicles according to FIG. 1 has a multi-circuit master cylinder 2 of a known type connected to a brake booster 1 . The multi-circuit master cylinder 2 is connected to a pressure medium container 3 . From the multi-circuit master cylinder 2 take brake lines 4 from a different brake circuit space ; 4 a their output, one of which each has a lock-protected wheel brake cylinder 5 , 5 a ; 6 , 6 a leads a brake circuit. The brake lines 4 , 4 a each lead to an electromagnetically actuated second valve arrangement 7 ; 7 a and from there to an electromagnetically actuated first valve arrangement 8 , 8 a ; 9 , 9 a each of a brake circuit, each in a through position 10 , 10 a ; 11 , 11 a a connection to at least one wheel brake cylinders 5 , 5 a ; 6 , 6 a can produce. The first valve assemblies 8 , 8 a ; 9 , 9 a can be formed by 3/3 valves or 2/2 valves.

In the through positions 10 ; 10 a , 11 , 11 a of the first valve arrangement 8 , 8 a ; 9 , 9 a are blocking connections 12 , 12 a ; 13 , 13 a closed, alleviate during the pressure reduction from the wheel brake 5 , 5 a ; 6 , 6 a a connection to a brake circuit assigned pump pistons 15 , 15 a ; 16 , 16 a and cylinder rooms 19 , 19 a ; 21 , 21 a can be switched. The pump pistons 15 , 15 a ; 16 , 16 a at least one brake circuit rests on an actuating piston 18 connected to a control valve arrangement 17 with a broken line. The actuating piston 18 can be shifted alternately by the application of pressure medium by means of the control valve arrangement 17 , a first 40 and a second valve element 50 being opened and closed in the opposite direction.

In a shift direction which is the pump piston 16 associated with the cylinder chamber 19 via an opening in the direction of the multiple-circuit master cylinder 2 check valve 20 with a conduit member 25 and a feeding point 26 a connected brake line 4 a with a brake circuit space of the multiple-circuit master cylinder 2 and at the same time with the in a closed position 27 brought second valve assembly 7 verbun, during which the pump piston 16 a associated cylinder space 19 a over a in the direction of the cylinder space 19 a opening Rückschlagven valve 28 a and a leading to the first valve assemblies 9 , 9 a of a brake circuit line 29 a in the pressure reduction position at least a first valve arrangement 9 , 9 a is connected to at least one wheel brake cylinder 6 , 6 a . The graduated actuating piston 18 is in this direction of displacement from a pressure medium beatable first piston shoulder 30 , which extends from an inner wall 31 of a graduated hydraulic chamber 41 to a he most lateral surface 32 of the actuating piston 18 of substantially smaller diameter, against averted and with Pressurizable second piston shoulder 33 of the actuating piston 18 , which extends from the inner wall 31 of the hydraulic chamber 41 to a second lateral surface 34 of the actuating piston 18 with a larger diameter than that of the lateral surface 32 , has been moved.

One of the first piston shoulder 30 of the actuating piston 18 facing the first hydraulic chamber section 53 is connected to a line 36 through the first valve element 40 of the control valve arrangement 17 to an outlet side 42 of a self-priming pressure medium pump 43 . The pressure medium pump 43 is connected to an inlet side 44 with a reservoir 45 . One of the second piston shoulder 33 of the actuating piston 18 facing the second hydraulic chamber section 54 is connected with a line 47 between the output side 42 of the pressure medium pump 43 and the first valve element 40 of the control valve arrangement 17 to the line 36 with a feed point 48 .

From the line 36 branches between the first hydraulic chamber section 53 and the first valve element 40 of the control valve assembly 17, a second valve element 50 having and downstream of the line part 49 opening into the reservoir 45 .

The actuating piston 18 is moved in a different direction of displacement by the pressure force of the pressure medium acting on the second piston shoulder 33 of the actuating piston 18 , which then opposes a pressure which acts substantially less on the first piston shoulder 30 of the actuating piston 18 .

The first hydraulic chamber section 53 is connected by the opening position 57 in a second valve element 50 to the storage tank 45 , while the first valve element 40 is switched to a closed position 56 .

The pump pistons 15 ; 16 are on the acting as a piston pump Be actuating piston 18 on one of the first piston shoulder 30 facing away from the first end face 58 by in the cylinder spaces 19 ; 21 arranged compression springs 51 ; 52 created. The pump pistons 15 a ; 16 a are in the cylinder rooms 19 a ; 21 a arranged compression springs 51 a ; 52 a is applied to a second end face 60 of the actuating piston 18 facing away from the second piston shoulder 33 . The end faces 58 , 60 who in their dimensions preferably ausgebil det with the diameter of the first 32 and second lateral surface 34 of the actuating piston 18 .

Due to the alternating movement of the actuating piston 18 , a specific air volume in this air volume accommodating compensation spaces 59 , 61 is displaced and sucked through an end face 58 , 60 . The compensation spaces 59 , 61 are formed with inlet and outlet channels 62 , 62 a , 63 , 63 a , which are connected to the atmosphere.

For the actuating piston 18 , damper elements for the respective end positions are introduced in the hydraulic chamber sections 53 , 54 .

In one embodiment, opposite to the piston shoulders 30 , 33 of the actuating piston 18 in side walls fixed to the housing 22 , 23 damping chambers 38 , 39 in the form of a cylinder jacket are arranged, which cooperate with piston stages 30 , 33 attached to the piston shoulders 101 , 102 in such a way that during a thaw Chen the piston stages 101 , 102 in the damper chambers 38 , 39 a hy draulic damping of the actuating piston 18 is carried out alternately.

The conveyor designed as a piston pump is next to the Use for the anti-lock control case also for the drive slip rule applicable.

At least one further pump piston 68 arranged in one direction of the actuating piston 18 is attached in a cylinder space 67 . The pump piston 68 is also applied to the pump as a piston-acting actuator piston 18 by means disposed in the cylinder chamber 67 pressure spring 64th The cylinder chamber 67 is there in a direction of displacement via a line 91 with a line 69 in connection, which is connected to the brake line 4 a between the first 9, 9 a and the second valve arrangement 7 , and thus with the first valve arrangement 9 , 9 opened a directly with the wheel brake cylinder 6 , 6 a .

Averted from the first valve arrangement 9 , 9 a , the line 69 is provided with a third valve arrangement 81 after the branching of the line 91 and leads to the pressure medium container 3 . In a bypass line 82 connected to the line 69 and bypassing the third valve arrangement 81 , a check valve 83 closing in the direction of the pressure medium container 3 is arranged.

If the second valve arrangement 7 is switched to the closed position 27 and the third valve arrangement 81 to a closed position 97 , pressure medium can be drawn from the cylinder space 67 into the line 69 and a line section 71 connected to it through one of the first valve arrangements 9 ; 9 a in one of the wheel brake cylinders 6 ; 6 a and simultaneously through both first valve assemblies 9 , 9 a in both wheel brake cylinders 6 , 6 a are promoted. In line 69 of the line section 71 and the intersection is the Lei tung 91 log-9 a öff nendes check valve 93 arranged in the direction of the first valve arrangements 9 between the branch. The Radbremszylin 6 , 6 a are assigned to a brake circuit and a drive axle.

If the drive wheels are assigned to two brake circuits, a line part 73 branches off from a feed point 72 on the line 69 between the third valve arrangement 81 and the check valve 93 with a check valve 79 opening in the direction of the other brake circuit, which connects with the brake line 4 of the other Brake circuit is connected in which the first valve assemblies 8 , 8 a of the other brake circuit are located, which can be switched to different positions.

If a hydraulic brake booster 1 is used in the brake system, a line part 74 connected to the brake booster 1 is connected to the line 36 between the pressure medium pump 43 and the first valve element 40 . In the conduit portion 74 a of hydraulical the brake booster 1 is placed associated pressure with telspeicher 80 which can be filled when it falls below a given reservoir pressure of the pressure medium pump 43 with pressure medium. A return line 76 connected to the brake booster 1 is connected to the reservoir 45 .

In the embodiment of FIG. 2, the same reference numerals are used for the same and equivalent components as in the first exemplary embodiment from FIG. 1.

In FIG. 2 8, the first valve arrangements 8, a; 9 , 9 a designed as 2/2 solenoid valves. The brake lines 4 ; 4 a , each starting from a different brake circuit space of the multi-circuit master cylinder 2 , each lead to an electromagnetically actuated fourth valve arrangement 84 ; 84 a and from there through one of the second valve arrangements 7 ; 7 a to the first valve arrangements 8 , 8 a ; 9 , 9 a .

In the brake lines 4 ; 4 a between the fourth valve arrangements 84 ; 84 a and the second valve arrangements 7 ; 7 a not only leads to a line section 85 ; 85 a , which is connected to one of the cylinder spaces 19 a , 21 a , but via one feed point 86 ; 86 a also a connecting line 87 ; 87 a to each of the cylinder rooms 19 ; 21st

In the embodiment according to FIG. 3, the same reference numerals are used for the same and equivalent components as in the exemplary embodiments according to FIGS . 1 and 2.

In Fig. 3, the conveyor 90 is formed for each of the brake circuits with two pump pistons 16 , 16 a for the anti-lock control case, the opposite end faces 58 , 60 of the actuating piston 18 are displaceable. A third pump piston 89 is used to control the traction slip, is applied in series to the pump piston 16 a and is moved by it.

In the exemplary embodiment according to FIG. 4, in deviation from the exemplary embodiment according to FIG. 3, each pump piston 16 ; 16 a and each associated cylinder space 19 ; 19 a to a brake line 4 ; 4 a of another brake circuit connected. In the line section 71 between the second valve arrangement 7 and the first valve arrangement 9 ; 9 a , a receiving chamber 92 is arranged. The first Ven valve arrangements 9 , 9 a can be designed as 2/2 solenoid valves or as 3/3 solenoid valves.

The operation of the ordinary brake system is known and remains unaffected by a certain Ven tilanordnung as well as the arrangement of the conveyor 90 in the overall system during a braking operation. If one of the wheels tends in the exemplary embodiment according to FIG. 1 or if several wheels tend to lock together, sensors which are arranged on the wheels are known to give signals to an electronic control unit, through which the corresponding first valve arrangements 8 , 8 a ; 9 , 9 a controlled electromagnetically and switched from the pressure build-up position to a second pressure holding position or to a third pressure reduction position, by means of which a certain pressure modulation in the wheel brake cylinders 5 , 5 a ; 6 , 6 a results. With the valve excitation, the pressure medium pump 43 is switched on in order to be able to actuate the conveyor device 90 by the control valve arrangement 17 . Arranged in the conveyor 90 the pump piston 15, 15 a; 16 , 16 a can now be connected to at least one wheel brake cylinder in the respectively assigned brake circuit by at least one of the first valve arrangements.

In the case of the wheel brake cylinder 6 , the first valve arrangement 9, consisting of a 3/3 solenoid valve, switches to a closed position 95 while the pressure is being maintained, and the other first valve arrangement 9 a can remain in a through position 11 a . Must then be reduced in the pressure in the wheel brake cylinder 6 , the first Ventilanord voltage 9 is switched to a pressure reduction position 96 , and the pump pistons 16 , 16 a remove in a direction of displacement via the check valves 28 , 28 a and the line 29 a , the a feed point 88 leads to a first valve assembly 9 , 9 a , excess gewor denes pressure medium volume from the wheel brake cylinder 6 and promote it in another direction of displacement via the check valves 20 , 20 a in the line part 25 and from there into the master cylinder with the multi-circuit 2 connected line 4 a back. The second valve arrangement 7 remains in an open position.

Will when starting one of the wheels to serve its propulsion to stand, so this is detected in a known manner by a sensor and passed on by a signal from the electronic control unit to at least one associated with a drive wheel first valve assembly. The wheel brake cylinders 6 , 6 a of a brake circuit can be assigned to the drive wheels and can be used individually and together.

If the drive wheels are arranged in two brake circuits, the first valve arrangements 8 and 9, for example selected, with the associated wheel brake cylinders 5 and 6 can also be regulated individually or together via the line part 73 .

During a traction control system in a brake circuit, the pressure medium pump 43 is also switched on and the pump piston 68 , 89 is actuated in the manner described by the actuating piston 18 , so that pressure medium flows into at least one wheel brake cylinder because the second valve arrangement 7 and the third valve arrangement 81 are switched into closed positions 27 , 97 and pressure medium is sucked in via the check valve 83 from the pressure medium container 3 and is conveyed by the pump piston 68 , 89 .

If a pressure build-up in the wheel brake cylinders assigned 6 , 6 a is only required in the one wheel brake cylinder 6 , the wheel brake cylinder 6 a assigned first valve arrangement 9 a is switched into a locked position to the wheel brake cylinder 6 a .

If a buildup of pressure in two brake circuits required in a drive slip control operation, the to the driving wheels belonging to the wheel brake cylinders 5, 6 characterized charged with pressure medium in that adjacent to the second valve assembly 7 and the third valve arrangement 81 a is switched to the closed position 27a and the other second valve arrangement 7 is and the line part 73 establishes the connection to the other brake circuit.

During a traction control process, an undesirably high pressure value can arise in line 69 . A connected with the bypass line 82 between the cylinder space 67 and check valve 83 further bypass line 77 leads to a pressure relief valve 78 which opens at a maximum operating pressure of the check valve 83 in the direction of the pressure medium container 3 .

After the traction control process has ended, the second valve arrangements 7 ; 7 a and the third valve arrangement 81 switched back into their open positions.

The control valve assembly 17 is controlled for the anti-lock control process and for the traction control process together with the Druckmit telpumpe 43 by an electronic control device of a known type. Here, a connection between the pump 43 and the opposing first 53 and second cylinder is alternately chamber portions 54 on the actuating piston 18, as prepared between the second cylinder chamber portion 54 and the pressure medium pump 43 and the first cylinder chamber portion 53 and the reservoir 45th

The oppositely attached active surfaces of the first piston shoulder 30 and the second piston shoulder 33 of the actuating piston 18 are formed in their dimensions in an order of magnitude adapted to the performance of the anti-lock control system.

The anti-lock control system can be operated with two pressure media. A pressure medium can be used between the pressure medium pump 43 and the conveyor 90 . Another medium pressure medium can be used between the conveyor 90 and the brake system.

In Fig. 2, an arrangement is shown in which the first valve arrangements 8 , 8 a ; 9 , 9 a consist of 2/2 solenoid valves. If a certain pressure modulation on the brake circuit associated with the first valve arrangement 9 is required, the fourth brake arrangement 84 a assigned to the same brake circuit is switched into a closed position 98 , and the other first valve arrangement 9 a also assumes a closed position 99 . The first valve assembly 9 is thus via the second valve arrangement 7 in the open position with the cylinder spaces 19 , 19 a connected to the conveyor 90 , pressure medium being removed from the first valve assembly 9 and conveyed in the direction of the multi-circuit master cylinder 2 leading brake line 4 a can be.

In Fig. 3, an arrangement is shown in which the Förderein direction 90 consists of two pump pistons 16 , 16 a for the anti-lock control usually a brake circuit. A further conveyor 90 must be added to the brake system for the arrangement of a second brake circuit that is controlled by an anti-lock and drive slip. The pump piston 89 applied in series to the pump piston 16 a is provided for traction control. An associated cylin derraum 94 is formed with a pressure medium inlet 66 and with a pressure medium outlet 70 . The pressure medium inlet 66 is connected via the line 69 and the bypass line 82 with the check valve 83 opening in the direction of the cylinder space 94 and can thus be placed on the connected line to the pressure medium container 3 .

The pressure medium outlet 70 is connected via line 69 and the check valve 93 to the brake line 4 a between the second valve arrangement 7 and the first valve arrangement 9 . Through him pressure medium to one of the first valve assemblies 9 ; 9 a or promoted to both first valve assemblies 9 , 9 a .

In the embodiment according to FIG. 4, pressure medium is from only one pump piston 16 ; 16 a from only one brake circuit 4 ; 4 a can be removed in case of anti-lock control. In a quickly perform the pressure reduction from the wheel brake cylinders 6 , 6 a pressure medium can first be taken up by the receiving chamber 92 before it is promoted ge by the conveyor 90 in the direction of the multi-circuit master cylinder 2 .

Claims (20)

1. Anti-lock control system for vehicles, the wheels of which are each assigned a wheel brake cylinder connected via a brake line to a multi-circuit master cylinder, with at least one egg nem assigned to the anti-lock wheels and located in the brake line, the first valve arrangement in the anti-lock control switching positions at least for pressure build-up and pressure reduction can take on a wheel brake and at least one of the brake circuits associated conveyor, which can receive a medium flowing back from the first valve assembly under pressure reduction pressure and delivers towards the brake line, characterized in that a piston pump serves as the conveyor ( 90 ), the has an actuating piston ( 18 ) which can be acted upon by pressure medium which, in the event of an anti-lock control, alternately from a control valve arrangement ( 17 ) in a first or a second net to one side of the actuating piston ( 18 ) en hydraulic chamber section ( 53 , 54 ) is guided and thereby displaces the actuating piston ( 18 ) in such a way that at least two actuating pistons ( 18 ) bearing pump pistons ( 15 , 15 a ; 16 , 16 a ) at the same time in cylinder rooms ( 19 , 19 a ; 21 , 21 a ) are actuated, which in their one direction of displacement via check valves ( 28 , 28 a ) suck pressure fluid from the wheel brakes into the respective cylinder space and in their other direction of displacement Druckmit tel via other check valves ( 20 , 20 a ) from the respective cylinder space ( 19 , 19 a ; 21 , 21 a ) in the brake line ( 4 , 4 a ). 2. Anti-lock control system according to claim 1, characterized in that the control valve arrangement ( 17 ) from a first Ventilele element ( 40 ) and a second valve element ( 50 ) and the first valve element ( 40 ) in a line ( 36 ) from a pressure medium pump ( 43 ) to which one side of the actuating piston ( 18 ) is assigned the first hydraulic chamber section ( 53 ) and the second valve element ( 50 ) is arranged in a line part ( 49 ) which is separated from the line ( 36 ) between the first valve element ( 40 ) and which he branches most hydraulic chamber section ( 53 ) and leads to a Vorratsbe container ( 45 ) and that the other side of the actuating piston ( 18 ) associated second hydraulic chamber section ( 54 ) has a smaller effective area and with the line ( 36 ) between the pressure medium pump ( 43 ) and the first valve element ( 40 ) is connected via a line ( 47 ), the first for actuating the actuating piston ( 18 ) ( 40 ) and the second valve element ( 50 ) can be opened and closed in the opposite direction. 3. Anti-lock control system according to claim 2, characterized in that on the line ( 36 ) between the pressure medium pump ( 43 ) and the first valve element ( 40 ) of the control valve arrangement ( 17 ) with a pressure medium accumulator ( 80 ) provided line part ( 74 ) is connected is, which leads to a brake booster ( 1 ). 4. Anti-lock control system according to claim 1, characterized in that in the traction control case of the actuating piston ( 18 ) of the type via the control valve arrangement ( 17 ) with pressure medium can be acted upon in that the pressure build-up in the wheel brake cylinders ( 5 , 5 a ; 6 , 6 a ) a further pump piston ( 68 ) abutting the actuating piston ( 18 ) can be actuated, is displaceably mounted in a cylinder space ( 67 ) and, in the event of traction slip control, is connected in one direction of displacement to a pressure medium supply source and in another direction of displacement to build up pressure via the first valve arrangement ( 8 , 8 a ; 9 , 9 a ) is connected to at least one wheel brake cylinder ( 5 , 5 a ; 6 , 6 a ). 5. Anti-lock control system according to claim 4, characterized in that the control valve arrangement ( 17 ) consists of a first Ventilele element ( 40 ) and a second valve element ( 50 ) and that the first valve element ( 40 ) in a line ( 36 ) from a Druckmit telpump ( 43 ) to which the first hydraulic chamber section ( 53 ) is arranged on one side of the actuating piston ( 18 ) and the second valve element ( 50 ) is arranged in a line part ( 49 ) which is separated from the line ( 36 ) between the first valve element ( 40 ) and the first hydraulic chamber section ( 53 ) branches off and leads to a storage container ( 45 ) and that the other side of the actuating piston ( 18 ) associated with the second hydraulic chamber section ( 54 ) has a smaller effective area and with the line ( 36 ) between the pressure medium pump ( 43 ) and the first valve element ( 40 ) is connected via a line ( 47 ), the first ( 18 ) for actuating the actuating piston ( 18 ) 40 ) and the second valve element ( 50 ) can be opened and closed in the opposite direction. 6. An anti-lock control system according to claim 4, characterized in that to build up pressure in the cylinder chamber ( 67 ) to at least one wheel brake cylinder ( 5 , 5 a ; 6 , 6 a ) of a brake circuit leading line ( 69 , 73 ) in the traction slip control case at least a second ( 7; 7 a) in the connection between the multi-circuit master cylinder ( 2 ) and the first valve arrangements ( 8 , 8 a ; 9 , 9 a ) attached valve arrangement in a closed position ( 27 ; 27 a ) and one in a connection between the Cylinder chamber ( 67 ) and a pressure medium container ( 3 ) arranged third valve arrangement ( 81 ) is also switched to a closed position ( 97 ). 7. Anti-lock control system according to claim 6, characterized in that in the case of traction control a line ( 91 ) between the cylinder chamber ( 67 ) of the pump piston ( 68 ) and the closed position ( 97 ) third valve arrangement ( 81 ) with a by-pass line ( 82 ) is connected, which is still connected to the pressure medium container ( 3 ) by a check valve ( 83 ) opening in the direction of the cylinder space ( 67 ). 8. Anti-lock control system according to claim 1, characterized in that a bypass line ( 82 ) between a cylinder space ( 67 ) and a check valve ( 83 ) connected bypass line ( 77 ) leads to a pressure medium container ( 3 ) and a pressure relief valve ( 78 ). 9. anti-lock control system according to claim 8, characterized in that the pressure relief valve ( 78 ) opens in the traction control case at a value above the maximum permissible operating pressure in the direction of the pressure medium container ( 3 ). 10. Anti-lock control system according to claim 4, characterized in that in the traction control case in the line between the cylinder chamber ( 67 ) of the pump piston ( 68 ) and at least one wheel brake cylinder ( 6 , 6 a ) of a brake circuit a connection leading to another brake circuit ( 72 , 73 ) and can be connected to at least one other wheel brake cylinder ( 5 , 5 a ). 11. Anti-lock control system according to claim 1, characterized in that at least one pump piston ( 89 ) for traction slip is usually arranged in series with one of the pump pistons ( 16 , 16 a ) for the anti-lock control case. 12. Anti-lock control system according to one of claims 1, 4 or 11, characterized in that at least two pump pistons ( 15 a , 16 a , 68 , 89 ) can be actuated simultaneously in the same direction of action. 13. Anti-lock control system according to claim 12, characterized in that at least two pump pistons ( 15 a , 16 a , 68 ) are arranged parallel to one another. 14. Anti-lock control system according to claim 1, characterized in that the first valve arrangements ( 8 , 8 a ; 9 , 9 a ) consist of 3/3 solenoid valves. 15. Anti-lock control system according to claim 1, characterized in that the first valve arrangements ( 8 , 8 a ; 9 , 9 a ) consist of 2/2-solenoid valves. 16. Anti-lock control system according to claim 1, characterized in that the actuating piston ( 18 ) has piston shoulders ( 30 , 33 ), the effective surfaces acted upon by pressure medium are of different sizes. 17. Anti-lock control system according to claim 1, characterized in that the pressure medium used for the brake circuits is different from the pressure medium used to actuate the actuating piston ( 18 ). 18. Anti-lock control system according to claim 1 or 4, characterized in that in the cylinder spaces ( 19 , 19 a ; 21 , 21 a ; 67 ) compression springs ( 51 , 51 a ; 52 , 52 a ; 64 ) are arranged, which to the Engage the pump piston ( 15 , 15 a ; 16 , 16 a ; 68 ) and place them on the end faces ( 58 , 60 ) of the actuating piston ( 18 ). 19. Anti-lock control system according to claim 1, characterized in that a pump piston ( 16 ; 16 a ) is connected to a brake line ( 4 ; 4 a ) each having a brake circuit. 20. Anti-lock control system according to claim 19, characterized in that in a connection between the multi-circuit master cylinder ( 2 ) and the first valve arrangements ( 9 , 9 a ) a second valve arrangement ( 7 ; 7 a ) is provided and in a line ( 71 ) between the second valve arrangement ( 7 ; 7 a ) and the first valve arrangements ( 9 , 9 a ) a receiving chamber ( 92 ) is arranged.